Vehicle cooling fan

ABSTRACT

A cooling fan for a vehicle. Many engine compartments of motor vehicles are small in size, and contain numerous components. Electric cooling fans are used to draw air through a radiator. Given the cramped conditions within the engine compartment, the exhaust of the fan cannot be directed into open air, but must impinge on one or more of the components within the compartment. This situation reduces velocity in the exhaust, and also reduces efficiency of the fan. The invention provides a collection of generally co-axial stators which divert the exhaust around the components, while retaining much of the velocity of the exhaust.

BACKGROUND OF THE INVENTION

In modern motor vehicles, the engine compartment is becoming increasingly crowded, primarily because of (1) the placement of additional components into the engine compartment, (2) the reduction in volume of the engine compartment, primarily to reduce overall aerodynamic drag of the vehicle, and many other factors.

The crowded nature of the compartment can cause problems in the operation of a cooling fan, such as that illustrated in FIG. 1. Fan 3 draws air 4 through a heat exchanger 6, commonly termed a radiator, thereby cooling the liquid coolant within the radiator 6. However, if, as on the right side of FIG. 1, an obstruction 9 is positioned within the exhaust of the fan 3A, the obstruction 9 can reduce flow through the radiator, thereby reducing cooling.

The invention presents a stratagem for reducing the negative effects of the obstruction 9.

SUMMARY OF THE INVENTION

An object of the invention is to provide an improved cooling fan for a vehicle.

A further object of the invention is to provide a cooling fan for a vehicle which operates efficiently in a confined environment.

In one form of the invention, stators are positioned in the exhaust stream of a cooling fan in a motor vehicle. The stators divert air into the radial direction, while increasing total airflow over the situation wherein the exhaust stream impinges on an obstacle it its path.

In one aspect, one embodiment comprises an apparatus, comprising: a fan which produces an exit flow; and vanes upstream of the obstacle which divert a portion of the exit flow into a radial direction.

In another aspect, one embodiment comprises an apparatus; comprising: a vehicle; within the vehicle, a cooling fan which generates a generally cylindrical airflow toward an obstruction downstream of said fan; and one or more stators between said fan and said obstruction, which turn generally axially flowing air into generally radially flowing air.

In still another aspect, one embodiment comprises an apparatus comprising: a generally axial-flow fan which produces exhaust having polar coordinates (r, z, theta) definable therein; vanes present in the exhaust, which increase radial component of the exhaust; and wherein vanes at different coordinates (r, theta, z) have different geometries.

In yet another aspect, one embodiment comprises an apparatus; comprising: a generally axial-flow fan which produces an exhaust, and means present in the exhaust for reducing a change in angle-of-attack of blades in the fan, which change is caused by an obstacle in the exhaust.

In another aspect, one embodiment comprises an apparatus; comprising: a cooling system; a generally axial-flow cooling fan for use in a vehicle having an obstruction in said vehicle downstream of the cooling fan which, if exhaust of the fan is allowed to reach the obstruction unimpeded, diverts the exhaust into radial directions with an average speed V1, and a set of stators between the fan and the obstruction, which divert the exhaust into radial directions with an average speed V2, higher than V1.

In yet another aspect, one embodiment comprises a method for improving cooling of an engine in a vehicle, said method comprises the steps of: situating a set of stators or vanes in an airflow path between a fan and an obstruction to diver exhaust into a generally reclined direction at a speed that exceeds the speed at which airflow is diverted by said obstruction.

These and other objects and advantages of the invention will be apparent from the following description, the accompanying drawings and the appended claims.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 illustrates a prior-art fan used to cool a component in a vehicle;

FIG. 2 illustrates the general location of the invention within the vehicle environment;

FIG. 3 illustrates a fan used in FIG. 2;

FIGS. 4 and 5 illustrate one form of the invention;

FIG. 6 is a cross-sectional view of part of FIG. 4 or 5;

FIG. 7 is a three-dimensional view of turning of air, which occurs in FIG. 6;

FIG. 8 illustrates one of the stators of FIGS. 4 and 5, in perspective view;

FIGS. 9-12 are plots of velocities and pressure contours that illustrate effectiveness of the stator vanes of FIGS. 4 and 5;

FIGS. 13-15 illustrate flow vs pressure, flow vs input torque, and efficiency of the invention;

FIG. 16 is a schematic of a blade B of a fan 200;

FIG. 17 is a vector diagram illustrating two airstreams 210 and 220 seen by blade B of FIG. 16;

FIG. 18 illustrates the vector sum 225 of the vectors in FIG. 17;

FIG. 19 illustrates how the vector sum 225 changes if the vector 220 changes;

FIG. 20 illustrates a velocity profile of air which encounters a blockage, in the absence of turning vanes;

FIG. 21 illustrates a velocity profile of air which encounters a blockage, with turning vanes V present;

FIG. 22 illustrates a standard cylindrical coordinate system;

FIGS. 23, 24, and 26 illustrate different forms of the invention;

FIG. 25 illustrates two locations P3 and P6, at the 3 o'clock and 6 o'clock positions, respectively;

FIG. 27 illustrates two sectors S1 and S2 in a fan; and

FIG. 28 illustrates vanes occupying part of sector S1.

DETAILED DESCRIPTION OF THE INVENTION

FIG. 2 illustrates a generalized motor vehicle 15, which contains an element 18, such as a gasoline engine, which requires cooling. Block 21 represents a cooling system, which is shown in greater detail in FIG. 3.

In FIG. 3, a fan 24, which is preferably, but not limited, to being driven by an electric motor (not shown), and preferably runs at a relatively constant speed, draws airstreams 22 through a radiator 30. An obstruction 33 can be present in the exhaust of the fan 24. The invention utilizes stators 35 to divert air around the obstruction 33.

FIGS. 4 and 5 illustrate one type of fan 24 that can be used. Stators 36 are present in the exhaust of the fan 24 and function to turn the axial component and increase the radial component of the fan exhaust, as indicated in FIG. 6. It is emphasized that FIG. 6 is a fragmentary cross-sectional view; FIG. 7 illustrates the turning accomplished by the stators 36 in perspective view.

FIG. 8 illustrates a perspective view showing a cutaway drawn in wire frame illustration which is contained to show a cut away of one of the stators 36, but in exaggerated scale: the solid metal/plastic cross section is enlarged with respect to the diameter, to more clearly show the shape of the cross section.

As FIG. 6 indicates, the stators 36 can take the form of circular arcs, spanning 90 degrees, for example.

FIGS. 9-15 set forth test results and simulation results which illustrate selected properties of an embodiment of the invention. FIGS. 9-12 are tracings of digital computer maps produced by simulation software, and are thus approximate illustrations.

FIGS. 9 and 10 illustrate a cross section of the annular operating region of the fan blade 45, showing the exit plane of the fan blades themselves and an obstruction 48 which is downstream of the annular fan blade region. Wall section 51 of the obstruction 48 can be viewed as cooperating with wall section 54, to thereby form a radial exit flow path for the fan exhaust flow.

FIG. 9 illustrates profiles of total pressure within the system in relative units. Total pressure includes a static component and a dynamic component. A scale of relative pressures is shown as the column of numbers, with 79.00 at the top.

To aid in showing overall patterns, the arrows leading from the scale of relative pressures are labeled with round numbers, such as 1, 15, 35, and so on. These round numbers represent convenient approximate values. For example, the arrow labeled 60 originates at a point between 52.14 and 65.57 on the scale. The number 60 is a convenient intermediate value between those two numbers.

Two significant features of FIG. 9 are that (1) the highest pressure region (labeled 70) abuts the obstruction, and (2) the pressures diminish in the radial direction, as the sequence 60, 50, 35, and 15 indicates.

FIG. 10 is a plot similar to FIG. 9, but with the stator vanes V present. The highest pressure regions (labeled 70) lie on the concave sides of the vanes V.

Significantly, in FIG. 10, the region of next-highest pressure, that labeled 55, extends significantly farther outward in the radial direction than the corresponding region in FIG. 9, and the third pressure region, that labeled 40, extends virtually to the outer boundary 100.

Stated more precisely, FIG. 9 indicates that at the radially outermost point from the flow regime, pressure has dropped from about 70 to about 15 in positive units, or to about 20 percent of the maximal value of 70. In contrast, FIG. 10 indicates that the analogous pressure drop is to only about 40 units, which is about 60 percent of the maximal value.

Thus, under the invention, high total pressure is sustained for a longer radial distance from the fan tip diameter, compared with the case of FIG. 9.

FIGS. 11 and 12 are similar to FIGS. 9 and 10, but illustrate velocity maps. In FIG. 11, the highest velocity is just above 11.07 units, and drops to just above 5.34 units at the radially farthest point from the fan tip diameter region N.

In FIG. 12, in which the stator vanes V are present, the highest velocity is higher, at above 12.12 units, compared with FIG. 11. Further, the triangular region in FIG. 12 labeled with a value of about 11.02, and extending to the radially outermost flow region 105, has a value about equal to the highest velocity in FIG. 11.

That is, the highest velocity in FIG. 11 has a certain value, but which drops to about half that value at the radially outermost flow region 105. In contrast, the vanes in FIG. 12 produce a higher velocity, at roughly the same location, and at least 80 percent of that velocity (about 11.02/12.12) is sustained at the region 105.

The invention of FIG. 12 delivers a higher velocity air stream, such as that indicated as about 11.02 relative units in FIG. 12, for a longer radial distance than does the apparatus of FIG. 11, as a comparison of the region labeled 9.97 in FIG. 11 with that labeled 11.02 in FIG. 12 indicates.

FIGS. 13-15 provide additional test results. Three cases were considered in each plot, namely (1) a physical situation similar to that of FIGS. 9-12, but with no stators present, and no obstruction present (that is, with both stators and downstream blockage absent), (2) a similar physical situation, but with no stators present, but with the obstruction present (that is, with the ring stator absent), and (3) a similar physical situation, but with stators present and the obstruction present (that is, with the ring stators present).

FIG. 13 is a plot of non-dimensional pressure rise coefficient against non dimensional flow coefficient. The pressure coefficient is the ratio of fan static pressure rise divided by both fan RPM and Tip diameter squared. The Flow coefficient is the ratio of the airflow divided by both the speed and fan tip diameter. These coefficients convenient non-dimensional groupings that relate directly to measured static pressure rise and airflow performance.

These convenient non-dimensional groupings allow plots of different experimental setups to be compared directly. For example, if a different fan speed were used or a fan of a different diameter, the plots of those two situations could be compared directly with that of FIG. 13.

FIG. 13 shows that in all cases for a flow rate exceeding about 0.16, the invention provides a higher pressure rise. This pressure rise is a figure-of-merit for the type of fan in question, and the increase in pressure rise indicates better performance, particularly in view of the reduction in torque required to obtain that increase in pressure rise comparing the without vs with ring stator condition for operation above 0.225 flow coefficient.

The pressure rise drops as flow increases because, as flow increases, the dynamic component of the total pressure becomes larger. Because the Fig. reports static pressure, static pressure drops as flow increases.

FIG. 14 is a plot of torque drawn by or applied to the fan 24 by the motor driving the fan 24. Plot 120 indicates that, with no stators nor obstruction present, the torque behavior drops as flow increases.

Plot 125 indicates that, with the obstruction present, but no stators present, torque remains somewhat constant, with a slight rise at about 0.22 units of flow coefficient.

Plot 130 indicates that, with the obstruction present and the stators installed, torque drawn form the motor is about the same as for plot 125, up to about 0.21 units of flow coefficient. Then, torque behavior drops.

FIG. 15 is a plot of efficiency against flow coefficient. FIG. 15 can be derived from FIGS. 13 and 14. From a broad view, FIG. 13 indicates the power produced by the fan. FIG. 14 indicates the power required by the fan. Thus, a comparison of power produced with power required provides a measure of efficiency.

More precisely, efficiency is computed as (P*F)/T

-   -   wherein     -   P is the pressure coefficient in FIG. 13,     -   F is the flow coefficient in FIGS. 13, 14, and 15, and     -   T is the torque coefficient in FIG. 14.

For example, for a flow coefficient F of 0.2, the pressure coefficient P in FIG. 13 is about 0.075, for the case without both obstruction and stators. The torque coefficient T in FIG. 14 is about 0.029. (P*F)/T equals about (0.075* 0.2)/(0.029). Since the quotient 0.075/0.029 is just under 3.0, the answer is under 0.6, consistent with FIG. 15.

FIG. 15 indicates that efficiency of the configuration with both blockage and ring stators increases for all flow coefficients exceeding 0.16. Further, the amount of the increase is obtained from plots 150 and 155. The increase at point P1 is from about 0.1 to 0.3, or by about 300 percent. The increase at point P2 is from about 0.25 to 0.4, or by about 160 percent. The increase at point P3 is from about 0.42 to about 0.52, or about 125 percent.

A significant comparison can be made between curves 155 and 150. The condition without both stators and blockage is a curve of interest, but does not relate to an installed vehicle condition. Curve 150 shows higher efficiency than curve 155 for flow coefficient levels above 0.16. Typical on vehicle operating range for cooling fans of this type ranges from 0.16 at an idle condition to above 0.30 at higher vehicle speed operation. The combination of stators with the downstream blockage provides benefit throughout the entire on vehicle operating range

In one mode of operation, it is contemplated that the fan 24 operate above a flow coefficient of 0.25 at least 90 percent of the time.

Additional Considerations

1. The invention improves efficiency of the cooling system. FIG. 16 illustrates a generalized fan 200 which produces an exhaust stream 201. A single blade B is shown, which rotates in direction 205.

FIG. 17 is a cross section of blade B. Arrow 210 represents the incoming air velocity seen by the blade B, due to rotation alone. The action of the fan 200 itself induces an axial component of inlet flow velocity represented by arrow 220. The magnitude of arrow 220 with respect to arrow 210 will increase with increasing vehicle speed which by the action of higher levels of ram flow admitted by the fan 200.

The net incoming air seen by the blade B is the vector sum of the two components 210 and 220, indicated in FIG. 18. In general, for (1) a given rotational speed, which determines vector 210, and (2) a given vehicle speed, which determines vector 220, one (or more) specific blade shapes provide optimal efficiency of the fan 200.

However, the presence of the obstacle disrupts this optimal efficiency. While the particular mechanism of the disruption is complex, a simplified view is that the obstacle reduces the velocity of the air flowing through the fan 200. The disruption can be viewed as reducing the size of vector 220, as indicated in FIG. 19. The vector sum 225 is now different. The changes to the vector sum 225 can vary greatly depending on the location along the blade hub to tip span and the location and nature of the downstream obstacle.

In general, the fan 200 was not designed for this different vector 225, and efficiency is reduced.

FIGS. 20 and 21 are simulations illustrating how the invention mitigates the loss in efficiency caused by the obstacle. In FIG. 20, with no vanes present, the 5.5 meter-per-second profile line 230 is indicated. Arrow 235 points to a region where this velocity has been lost.

In contrast, in FIG. 21, with vanes V present, the velocity in that region is not reduced so greatly. Flow through the fan is maintained more closely to the optimal value.

2. The vanes in cross section can assume airfoil shapes. These shapes can be different at different circumferential locations around the fan.

FIG. 22 illustrates the fan 200, together with a polar coordinate system superimposed thereon. A z-axis is shown. The radial coordinate, r, is the distance from the z-axis. The angle theta is measured from a reference line 250. Point P, for example, has the coordinates (r, theta, z) of (4, 0, 10).

In general, the shapes of the vanes can be different at different coordinates. For example, in FIG. 23, vane V1 has a chord length C1, while vane V2 has a chord length C2. Different vanes can also have different axial lengths AX or different radial depths RD.

In FIG. 24, vane V5 has an inlet angle A. Vane V6 has a different inlet angle of zero. Vane V7 has an exit angle of ninety degrees. Vane V8 has a different exit angle A2.

In one embodiment, the inlet angles, or exit angles, or both, can be similar at similar angles theta, but at different angles theta, they can differ. For example, in FIG. 25, the angles in question can be similar at the 3 o'clock position P3. The angles in question can also be similar at the 6 o'clock position P6, but the former can be different from the latter.

In addition, the similar angles can span a range of positions. For example, the angles in question can be similar from 3 o'clock to 6 o'clock.

In FIG. 26, three vanes V are shown. The radial distance R1 between adjacent vanes V10 and V11 is different from the radial distance R2 between adjacent vanes V11 and V12.

In a related type of difference, the channel width W between different pairs of vanes is different: different pairs define different channel widths. The channel width W need not be constant. Thus, an average width can be considered, or the minimum or maximum width.

Similarly, an annulus can be defined in the exhaust of the fan. An annulus is a band between two circles of different diameter. For example, the rings of Saturn form an annulus. In one form of the invention, vanes can be present in all or part of an annulus of given inner diameter, but vanes may be absent from other annuli.

In FIG. 27, vanes can be present in one sector S1, but absent from another sector S2. In FIG. 28, vanes can be partially present in sector S1, as indicated by the hatching, which indicates the presence of vanes.

Therefore, in general, the airfoil shape of the vanes can be different, at different coordinates (r, theta, z). The difference includes the absence of vanes entirely at certain coordinates. The parameters of airfoil shape, such as chord length, thickness, inlet angle, and exit angle, are defined in the art of aerodynamics. As stated, these parameters can vary over the (r, theta, z) space.

Also, the vanes in the sector which covers the obstacle can be designed differently from vanes in other sectors. For example, in FIG. 28, the obstacle O is represented. Sector S1 covers the obstacle.

3. The vanes can be ring-shaped, with the larger-diameter rings closer to the fan, and the smaller-diameter rings farther from the fan.

4. In one embodiment, radial struts generically indicated by dashed block 300 in FIG. 24 support the vanes.

In many types of fans, such radial struts are shaped to re-direct exhaust air generated by the fan. For example, in FIG. 22, because of the rotation indicated by arrow 205, the airstream generated by the fan will have a velocity component in the tangential direction. The radial struts are shaped to re-direct this tangential air into the axial direction, that is, parallel with the z-axis.

In one form of the invention, this re-direction does not occur, is not desired, and the radial struts are not designed to perform this re-direction.

It is recognized that any time an object is placed in a flow stream, some re-direction will occur. For example, if a flow stream is moving East, and encounters an object, part of the flow stream will flow North, part South, and part upward.

Similarly, if a flow stream generated by a fan encounters a radial strut, part of the flow stream will flow slightly tangentially, to avoid the strut.

Nevertheless, under the form of the invention in question, the struts are not designed to enhance or decrease this minimal amount of tangential flow. Stated another way, the impact on tangential flow is sought to be minimal, and the radial struts designed accordingly.

5. The fan-vane system is designed to be mounted within an engine compartment of a vehicle. Block 350 in FIG. 22 represents a mounting means. For example, the mounting means can take the form of three flanges, each having a bolt hole, the bolt holes defining a triangle. With such three-point mounting, flexing of the vehicle does not impart torsion to the fan.

That is, with four-point mounting, the four points define a quadrilateral, such as a rectangle. Assume that the rectangle is vertical, facing south, and the two lower corners are anchored. If the left upper corner moves north, and the right upper corner moves south, then torsion is applied to the rectangle.

Such torsion does not occur in three-point mounting.

Numerous substitutions and modifications can be undertaken without departing from the true spirit and scope of the invention. What is desired to be secured by Letters Patent is the invention as defined in the following claims. 

1. An apparatus comprising: a) a fan which produces an exit flow toward an obstacle in the exit flow; and b) vanes upstream of said obstacle which divert a portion of the exit flow into a radial direction.
 2. The apparatus according to claim 1, wherein said fan, obstacle, and vanes are located in the engine compartment of a vehicle.
 3. The apparatus according to claim 2, wherein said fan draws cooling air through a heat exchanger which cools engine coolant and/or a condenser that cools refrigerant for the vehicle air conditioning system.
 4. The apparatus according to claim 1, wherein said fan is generally an axial flow type.
 5. The apparatus according to claim 1, wherein said vanes mitigate reduction in fan efficiency caused by the obstacle.
 6. The apparatus according to claim 4, wherein at least three vanes are present, and radial spacing between one pair of neighboring vanes is different from radial spacing between a second pair of neighboring vanes.
 7. The apparatus according to claim 1, wherein a plurality of said vanes have different chord lengths.
 8. The apparatus according to claim 1, wherein said fan is of the axial flow type and i) vanes which are relatively near the axis are relatively far from said fan, and ii) vanes which are relatively far from the axis are relatively near to said fan.
 9. The apparatus according to claim 1, wherein said vanes are generally ring-shaped, and larger diameter vanes are closer to said fan than smaller diameter vanes.
 10. The apparatus according to claim 1, wherein at least one of said vanes has an inlet angle IA-1 and another of said vanes has an inlet angle IA-2, different from IA-1.
 11. The apparatus according to claim 1, wherein at least one of said vanes has an inlet angle IA-1 and another of said vanes has an inlet angle IA-2, is equal to IA-1.
 12. The apparatus according to claim 1, wherein at least one vane has an exit angle EA-1 and another of said vanes has an exit angle EA-2, different from EA-1.
 13. The apparatus according to claim 10, wherein all inlet angles of said vanes at similar angular positions are similar.
 14. The apparatus according to claim 12, wherein all exit angles of vanes having similar angular positions are similar.
 15. The apparatus according to claim 1, wherein the fan is generally an axial-flow type and at least some vanes span an arc of less than 360 degrees.
 16. The apparatus according to claim 14, wherein vanes at different radii span different arcs.
 17. The apparatus according to claim 1, wherein radial struts support the vanes, and the radial struts do not significantly re-direct tangential exhaust from the fan into axial flow.
 18. The apparatus according to claim 1, wherein radial struts support the vanes, and re-direction of tangential exhaust from the fan into axial flow by the radial struts is minimal.
 19. An apparatus, comprising: a) a vehicle; b) within the vehicle, a cooling fan which generates a generally cylindrical airflow toward an obstruction downstream of said fan; and c) one or more stators between said fan and said obstruction, which turn generally axially flowing air into generally radially flowing air.
 20. The apparatus according to claim 19, wherein said fan, obstruction, and stators are located in the engine compartment of a vehicle.
 21. The apparatus according to claim 19, wherein said fan draws cooling air through a heat exchanger which cools engine coolant and/or a condenser that cools refrigerant for the vehicle air conditioning system.
 22. The apparatus according to claim 19, wherein said fan is an axial flow fan.
 23. The apparatus according to claim 19, wherein the said vanes mitigate reduction in fan efficiency caused by the obstacle.
 24. The apparatus according to claim 23, wherein at least three stators are present, and radial spacing between one pair of neighboring vanes is different from radial spacing between a second pair of neighboring vanes.
 25. The apparatus according to claim 19, wherein different ones of said stators have different chord lengths.
 26. The apparatus according to claim 19, wherein said fan has a central axis defined therein and i) stators which are relatively near the axis are relatively far from the fan, and ii) stators which are relatively far from the axis are relatively near to the fan,
 27. The apparatus according to claim 19, wherein said stators are generally ring-shaped, and larger diameter stators are closer to the fan than smaller diameter vanes.
 28. The apparatus according to claim 19, wherein one of said stators has an inlet angle IA-1 and another stator has an inlet angle IA-2, different from IA-1.
 29. The apparatus according to claim 19, wherein one stator has an exit angle EA-1 and another stator has an exit angle EA-2, different from EA-1.
 30. The apparatus according to claim 28, wherein all inlet angles of stators at similar angular positions are similar.
 31. The apparatus according to claim 29, wherein all exit angles of stators having similar angular positions are similar.
 32. The apparatus according to claim 19, wherein said fan is generally an axial-flow type and at least some stators span an arc of less than 360 degrees.
 33. The apparatus according to claim 32, wherein stators at different radii span different arcs.
 34. The apparatus according to claim 19, wherein radial struts support the stators, and the radial struts do not significantly re-direct tangential exhaust from the fan into axial flow.
 35. The apparatus according to claim 19, wherein radial struts support the stators, and re-direction of tangential exhaust from said fan into axial flow by the radial struts is minimal.
 36. An apparatus, comprising: a) a generally axial-flow fan which produces exhaust having polar coordinates (r, theta, z) defineable therein; b) vanes present in the exhaust, which increase radial component of the exhaust; and wherein vanes at different coordinates (r, theta, z) have different geometries.
 37. The apparatus according to claim 36 and further comprising a vehicle having an engine compartment, wherein the fan and the vanes are located in the engine compartment.
 38. The apparatus according to claim 36, wherein an obstacle is present in the exhaust, and the vanes divert exhaust around the obstacle.
 39. The apparatus according to claim 36, wherein inlet angles of vanes at a common angle theta are similar.
 40. The apparatus according to claim 36, wherein exit angles of vanes at a common angle theta are similar.
 41. The apparatus according to claim 36, wherein, at a given z-coordinate, vane geometry is non-uniform for all theta.
 42. The apparatus according to claim 36, wherein vanes at different r-coordinates span different angles theta.
 43. The apparatus according to claim 19, wherein adjacent vane pairs define a channel therebetween, and different channels have different widths.
 44. The apparatus according to claim 36, wherein a first vane of a first radius spans an arc A1, and a second vane of a second radius spans an arc A2, different from A1.
 45. An apparatus, comprising: a) a generally axial-flow fan which produces an exhaust, b) means present in the exhaust for reducing a change in angle-of-attack of blades in the fan, which change is caused by an obstacle in the exhaust.
 46. The apparatus according to claim 45, and further comprising a motor vehicle which carries said fan and the means in an engine compartment.
 47. An apparatus, comprising: a) a cooling system; b) a generally axial-flow cooling fan for use in a vehicle having an obstruction in said vehicle downstream of the cooling fan which, if exhaust of the fan is allowed to reach the obstruction unimpeded, diverts the exhaust into radial directions with an average speed V1, and c) a set of stators between the fan and the obstruction, which divert the exhaust into radial directions with an average speed V2, higher than V1.
 48. A method for improving cooling of an engine in a vehicle, said method comprising the steps of: situating a set of stators or vanes in an airflow path between a fan and an obstruction to divert exhaust in a generally radial direction at a speed that exceeds the speed at which airflow is diverted by said obstruction. 